Sliding vane pump



Feb. 28, 1950 E. e. SEASTROM 2,498,715

SLIDING VANE PUMP 6 Sheets-Sheet 1 Filed March 3, 1945 ZZ Wm view .5; AI; i

ib 6 JW I v Feb. 28, 1950 E. e. SEASTROM SLIDING VANE PUMP 6Sheets-Sheet 2 Filed March 3, 1945 Feb. 2 8, 1950 E. e. SEASTROM2,498,715

SLIDING VANE PUMP' Filed March 3, 1945 e Sheets-Sheet 5 5125. a; x17 9/[if 1 9 Feb. 28, 1950 E. e. SEASTROM 2,498,715

SLIDING VANE PUMP Filed March 3, 1945 6 Sheets-Sheet 4 451 I 29/ agvwe/wkvb Feb. 1950 1:. G. SEASTROM 2,498,715

SLIDING VANE PUMP 6 Sheets$heet 5 Filed March 3, 1945 W fy A i W 15 M49/ {-447 y i 9 ya. ff/4 46 4 11 Feb. 2 8, 1950 E. G. S'EASTROM2,498,715

SLIDING VANE PUMP Filed March 3, 1945 6 Sheets-Sheet 6 Patented Feb. 28,1950 SLIDING VANE PUltfl' Erik G. Seastrom, Easton, Pa asslgnor toTreadwell Engineering Company, Easton, Pm, a. corporation ofPennsylvania Application March 3,1945, Serial No. 580,871

28 Claims. 1

This invention relates to pumps and has for its general object theprovision of novel and improved pumps of the combined centrifugal anddisplacement type.

More particularly, it is an object of the invention to provide a novelcentrifugal and displacement pump which will afford substantiallyuniform flow, and which is economical to manufacture and maintain, theconstruction and arrangement of the parts being such that the pump maybe conveniently produced in small sizes for household or domestic use.This application is a continuation-in-part of my copending application,Serial No. 534,306, filed May 5, 1944, now abandoned.

The invention, in its preferred embodiment, contemplates the provisionof a rotary having a substantially cylindrical housing within which isdisposed an axially arranged impeller member having a radia1 vane, andan eccentrically disposed cylindrical ring or sleeve through which thevane extends and which is adapted to rotate simultaneously with theimpeller. The sleeve is internally tangent to the substantiallycylindrical impeller member and externally tangent to the inner wall ofthe housing. The impeller comprises a hollow axially disposed shaft orhub from which the radial vane or wing extends. The wing or vane memberis also hollow and communicates with the interior of the hub which isadapted to receive fiuid from the intake openings in the pump casing.The vane is provided with openings in its rear surface considering thedirection of movement, and fluid is discharged from these openings intothe successivel expanding and contracting receiving portions of thelune-shaped chambers provided between the cylindrical sleeve and therespective surfaces of the impeller hub and of the pump casing.

The fluid is constantly discharged from the shrinking or contractingportions of these luneshaped chambers ahead of the vane, throughopenings provided in the walls of the sleeve, which openings communicatewith passageways within the body of the sleeve and which finallydischarge through the outlet connections of the pump. These outletconnections include a centrifugal outlet chamber, preferably ofexpanding volume, wherein the fluid from the hollow eccentric sleeve isgiven further impetus toward the final outlet of the pump.

Other objects and features of novelty include the provision of novelsealing means for preventing communication between the several workingchambers of the pump as they fluctuate in volume; means for assistingthe movement of fluid through the passageway in the eccentric sleeve;means for increasing the centrifugal movement of the fluid in the outletchamber; and means for affording a positive mechanical connectionbetween the impeller and the eccentric sleeve to supplement, whennecessary, the hydraulic drive of the sleeve as will be understood asthe detailed description proceeds.

Still further novel features will be apparent when the followingspecification is read in connection with the accompanying drawings inwhich certain embodiments of the invention are illustrated by way ofexample.

In the drawings,

Figure 1 is a vertical transverse sectional view of a pump comprisingone embodiment of the invention:

Figure 2 is a similar view of the same pump with the impeller displacedfrom the position shown in Figure 1;

Figure 3 Ba vertical axial sectional view of the pump taken on line 3-3of Figure 2;

Figure 4 is an enlarged detail view in vertical transverse sectionshowing the inlet and outlet provisions for the working chambers of thepump;

Figure 5 is a fragmentary sectional view taken on line 55 of Figure 2;

Figure 6 is a transverse vertical sectional view of a pump comprisinganother embodiment of the invention, in which certain modifications inthe outlet means are introduced;

Figure 7 is a fragmentary axial view of the pump shown in Figure 6;

Figure 8 is aview in end elevation of the pump shown in Figure 6, but ona reduced scale;

Figure 9 is a diagram showing very clearly the way in which thelune-shaped chambers are divided into constantl varying intake anddischarge portions by the vane;

Figure 10 is a vertical, axial, sectional view of a still furthermodified form of the invention;

Figure 11 is a partial, transverse, sectional view through the maindisplacement chamber of the pump shown in Fig. 10;

Figure 12 is an end view of the eccentric, rotating ring or sleeveemployed in the pump shown in Figs. 10 and 11; a part of the end coverbeing broken away;

Figure 13 is a view in side elevation of the same sleeve, parts beingbroken away for the sake of clearness of illustration;

Figure 14 is a fragmentary, sectional view taken on line l4-I4 of Fig.10 and showing the slot and pivot connection between the impelling vaneand the sleeve;

Figure 15 is a fragmentary, sectional view on an enlarged scale of anovel combined fluid pressure and centrifugal sealing arrangement inconnection with the rolling contact between the impeller hub and theinner wall of the sleeve;

Figure 16 is a diagrammatic development of the sleeve and the expandingdischarge chamber, indicating the relative velocities and forces of thesleeve and liquid;

Figures 17 and 18 are views in end and side elevation respectively ofstill another form of eccentric sleeve for use in the novel pumpinstallatlon;

Figures 19, 20, and 21 are fragmentary, axial, sectional views of thevaned portion of the sleeve, taken respectively on lines I9l9, 20-20,and 2l-2l of Fig. 1'7;

Figure 22 is a view in vertical transverse section of a still furthermodification of the novel p Figure 23 is a horizontal sectional viewtaken substantially on line 23-23 of Figure 22;

Figure 24 is a view of the rotor member of the pump shown in Figure 22,with parts shown in section and parts in elevation;

Figure 25 is a fragmentary developed view of the discharge orificeportion of the rotor sleeve; and

Figure 26 is a view in elevation of the pump casing.

Referring more particularly to Figures 1 to 5, inclusive, of thedrawings, it will be seen that the pump casing designated generally bythe reference numeral comprises the body portion II, and the cover plateI2. The body portion H is hollowed out to provide a substantiallycylindrical housing 13 for the working members of the pump. A drivenrotor shaft extends through an opening IS in the vertical wall 11 of thehousing and this shaft is provided with a hollowed end portion I 8 whichprojects into an axial opening 19 in the cover plate H2. The cover plateis suitably secured to projecting flanges on the body portion H as bybolts or other securing means, such as those suggested at in Figure 8,in connection with the second illustrated embodiment. The body portion 1l of the pump casing 10 may be provided with suitable legs or pedestals22. A conventional stufiing box indicated at 23 surrounds the shaft I5adjacent the opening IS in the casing.

The hollow end portion I8 of the shaft l5, which passes through thehousing interior I3, is provided with a substantially circular hubmember which is rigidly secured thereon by any suitable means. Both thehub 25 and the shaft end l8 are slotted longitudinally to receive thehollow rectangular substantially radally extending vane 0r wing 21 whichconstitutes an essential element of the impeller of the pump, and toprovide communication between the interiors of the vane and hub. Theimpeller as a whole may be designated by the reference numeral 30 andwill be understood to comprise the hollow end portion 18 of the shaftl5, the hub 25, and the vane 21. The rear wall 32 of the vane 21.considered from the standpoint of the direction of movement of theimpeller (indicated by the arrows A), is provided with a plurality ofopenings 33.

A substantially circular ring or sleeve member 35 is disposed within theinterior l3 of the pump casing and is guided within annular grooves 36and slots 31 provided respectively in the wall I! of the casing and thecover plate 12. The sleeve 35 is eccentrically disposed with relation tothe interior of the housing and also with relation to the hub 25 of theimpeller 30, and a longitudinal slot 38 is provided in the sleeve 35through which the hollow vane 21 of the impeller extends with as close aclearance as practicable considering the relative movement of the parts.

At the line of tangency between the sleeve 35 and the circular wall 39of the housing, there is provided a strip of sealing material 40. For asimilar purpose, the outer surface of the hub 25 which comes in rollingcontact with the entire surface of the ring 35 is provided with acovering 42 of sealing material. This material extends nearly all theway around the hub 25 since the line of rolling contact between the huband the ring is continually changing, although the place of contact 43is fixed with relation to the pump as a whole (see Figure 2 of thedrawings). One end 44 of the sealing strip 42 is turned in and clampedbetween the vane 21 and the edge of the opening in the hub 25 throughwhich the vane extends. The other end 45 of the strip 42 is embedded andsecured to the hub adjacent an areaate depression 46 which is providedto accommodate the bulb-like enlargement 41 of the ring 35 adjacent theforward face of the vane 21. A cooperating sealing flap 48 may besecured at the edge of the slot 38 in the ring 35 near the rear face 32of the vane.

The hollow bulb edge 41 of the ring 35 is provided with intaken openings50 and 51 which open outwardly and inwardly of the ring respectively.The interior of the bulb end 41 rovides a longitudinal channel orpassageway 53 which opens through the end of the ring 35 which is guidedin the circular slot 31 in the cover plate 12, as clearly shown inFigure 5. An annular outlet chamber 55 is provided in the cover l2 anddischarge conduits may be applied to the threaded opening 56 of thechamber 55 as shown in Figure 3 of the drawings.

Inlet connections for the pump may be applied to the threaded opening 51disposed axially of the cover plate 12 and communicating directly withthe central opening 60 Within the shaft end l8, from which the fluidpasses into the hollow interior 6| of the vane 21.

During operation of the pump, the impeller 30 and the ring 35 arecontinually rotating. for example, in a clockwise direction as indicatedby the arrows A. It will be observed that there is provided alune-shaped chamber between the outer surface of the impeller hub 25 andthe interior surface of the ring 35 as indicated at 65 in Figure l ofthe drawings. In this figure, the lune-shaped chamber is undivided andfull of fluid. Between the outer surface of the ring 35 and the innerWall 39 of the casing, a second lune-shaped chamber 66 is provided. InFigure 1 it will be seen that this chamber is substantially bisected bythe vane 21. However, as the impeller moves in the direction of thearrow A, the right hand portion or segment 66A of the chamber 66 will bediminishing in volume while the left hand segment 663 will beincreasing. The liquid within the portion 66A is being forced throughthe opening 50 and into the passageway 53 of the bulb-like end 41 of theedge of the ring 35. At the same time, the liquid being throwncentrifugally from the axial inlet chamber 60 through the hollowinterior 6| of the vane 21 passes through the openings 33 in the wall 32of the vane and serves to fill the chamber portion 663 of the outer lune5F At the point shown in Figure 1, the entire lune 65 is at a neutralposition in which it is completely filled with liquid and is about todischarge it. It will be understood that as the vane rotates from thispositions, the lowermost openings 33 in the vane 21'will being todischarge into the inner lune-shaped chamber 65 while the outlet opening5| will being to receive the fluid from the other side of the lune 65.As the vane 21 reaches the lower vertical position, 180 displaced fromthe position shown in Figure 1, the chamber 65 will be substantiallyequally divided into intake and discharge portions. At this point theouter lune-shaped chamber 66 will be undivided and will be filled withfluid.

In Figure 2 of the drawings the vane 21 has advanced beyond the lowervertical position, fluid is being discharged through the majority of theopenings 33 into the portion 553 of the lune 65 and the opposite portion65A is discharging liquid through the opening 5I. A few of the outermostopenings 33 in the vane are beginning to discharge liquid into theportion 663 of the lune 66 and the greater part 66A of this lune isdischarging through the opening 50 in the ring 35. From this, thegeneral operation of the pump will be clearly understood. The vane 21 iscontinually and alternately discharging fluid through its rear wall intothe successively enlargin portions 653 and 66B in the inner and outerlune-like chambers and the front wall of the vane is continually pushingfluid ahead of it as the forward chamber portions 65A and 66A diminishdue to the eccentricity of ring 35. The fluid is thus being transferredby a combination of centrifugal action and displacement from theshrinking chambers. During this rotative movement the respectivechambers are sealed off by means of the sealing material 40, the end ofthe impeller 21 which has a close flt with the wall 39 of the casing,and the material 42. This latter strip of material is increased ineffectiveness by the centrifugal expansion thereof during operation.

The entire construction and operation of the displacement portion of thepump may be further clarified by an inspection of the diagram shown inFig. 9 of the drawings.

In Figures 6, 7, and 8 of the drawings, there is illustrated amodification of the pump shown in the earlier figures and constituting asecond embodiment of the invention. Many of the parts of this embodimentare quite similar to corresponding parts of the first embodiment andwill be designated by the same reference numerals with I added. Forexample, the pump casing is indicated at H0 and comprises the bodyportion III and the cover plate I I2. A shaft I I is connected withsuitable driving means and has a hollow end II8 through which the fluidis received into the central chamber I60. A hub I25 is fixed upon thehollow end II8 of the shaft and an impeller vane I21 is received withinregistering openings in the shaft end H8 and the hub I25. Dischargeopenings I33 are provided in the rear face of the vane through whichfluid may flow from the hollow interior I6I of the vane. The end of thevane, of course, has a sliding fit with the inner wall of the housingIII, and hub I25 is covered with sealing material I42 just as in thecase of the first embodiment.

An eccentric ring I35 has one end fitted within the groove I36 of thecasing portion III and its ment first described in that it is hollow,being provided substantially throughout its circumference with anapproximately annular chamber I53. This chamber I53 opens axiallythrough a plurality of oriflces I54 into the annular outlet chamber I55of the pump, which is contained within the cover plate or head II2. Anydesired or appropriate number of these openings I54 may be provided. Thechamber I55 tapers somewhat and is of greatest cross-section near thebottom of the pump where it discharges through tangential passageway I63into the discharge conduit which may be applied in the connection I56.The discharge of the fluid thus has some centrifugal eflect.

A longitudinal slot I33 is provided in the hollow ring or sleeve I35,for the accommodation of the vane or impeller element I21. The edges ofthe slot I36 are preferably curved to provide for the relative movementof the vane and ring during rotation around their different centers.Adjacent the rearward face of the vane I21 the slot I38 has a solid wallI58 but adjacent the forward will of the vane the edge of the slot hasits wall cut away as at I59. Portions of the 'side wall of the ring arealso cut away as at I50 and I5I, so as to receive fluid within thechamber I53 from the shrinking portions of the lune-shaped pump chambersI65 and I66. The operation of this embodiment of the pump will bereadily understood. The chambers I65 and I66 are successively divided bythe vane I21 into forward portions of diminishing capacity and rearwardportions of increasing capacity, the former being vented through theopenings I50 and I5I' to the interior of the ring and thence to theoutlet chamber of the casing, the latter being supplied with fluidthrough the openings I33 in the vane.

In order to equalize the pressure in the hollow ring I35 and the annulargroove I36, a series of openings I69 may be provided in the circular endwall of the ring. An anti-friction or wear strip I10 may also beprovided in the bottom of the groove if desired.

Instead of the simple sealing strip 40 suggested in th first embodimentof the invention, there is shown in Figs. 6 and 7 of the drawings apressure seal which utilizes the differences in pressure between thesection I66A and i663 of the outer lune I66. The lune section I66A aheadof the vane I21 is under somewhat higher pres sure than the section I66Badjacent the trailing face of the vane. To take advantage of thiscondition, a hinged packing or sealing member I40 is disposed within arecess I4I provided within the lower portion of the casing. The mem ber40 has a circular pintle portion I40A situated within the similarlyshaped portion MIA of the recess I4I. Thus, any pressure liquid from theworking chamber portion I66A which makes its way into the recess I willcause the hinged sealing member I40 to press firmly against the outerperiphery of the sleeve I35. It will be noted that the left-hand andinner part of the seal I40 is in communication with the chamber $63 oflower pressure. Thus, the difference in pressure in these two workingchambers is employed to make the seal I40 more effective.

A clean-out opening I4IB is provided at the lowest point of the recessHI and may be stopped by a suitable closure element (not shown).

Adjacent the openings I54, there are formed upon the end surface of thering or sleeve I35, a

series of vanes I15 which project into the ex- 7 panding centrifugalchamber I55 and aid in swirling the liquid within this chamber andeffecting the centrifugal action. Thus, it will be noted that th fluidpasses centrifugally through the hollow vane of the impeller; the actionin the lunes is mainlydisplacement; and the final discharge through theoutlet chamber I55 to the orifice I56 again has a centrifugal component.

The embodiment of the invention illustrated in Figs. 10-15 inclusive ofthe drawings will now be described. The pump casing or housing 2"! inthis example is made in three parts, a central section 2 and two endcover plates or castings 2I2 and 2l2A. These casing portions provide asubstantially cylindrical chamber 2I3 for the moving parts of thedisplacement portion of the pump. In this embodiment the drive shaft 2I5is driven by a, motor or other source of power, passes through thestuffing box 223, and through the opening 2I6 in the end casting 2I2 ofthe housing 2I0. The end portion of the shaft 2I5 is enlarged to formthe integral hollow hub portion 225, a substantially cylindrical chamber260 being provided within the hub and communicating through the endportion 2| 8 of the shaft with the inlet connection 251. The inletconnection 251 is preferably co-axially disposed with relation to thedrive shaft 2I5 and is secured to the end plate or casting 2 HA.

Interlocked with the hub 225 is the radiallyextending impeller vane 221,the vane being interlocked as indicated at 228.

As clearly shown in Figs. 11 and 14 of the drawings, the vane 221 isprovided with an outlet passageway 26I through which fluid from thecentral chamber 250 is centrifugally thrown radially outwardly into thelune-shaped displacement portions of the working chamber 2 I 3. Upon theopposite face of the vane 221, facing in the direction of rotation ofthe impeller, there are provided the recesses 229 which provide a sortof scoop which serves to aid in the withdrawal of liquid from thelune-shaped sections of the displacement chambers, and in directing thefluid into the mouth of the hollow eccentric which will be described.The impeller as a whole comprises the enlarged hollow hub 225 of theshaft 2I5, together with the interfitted vane 221, and this assembly inits entirety may be designated by the reference numeral 230.

The circular, eccentrically disposed hollow ring, in this embodiment, isindicated generally by the reference numeral 235 that is shown detachedfrom the pump housing in Figs, 12 and 13 of the drawings. An eccentric,circular groove 236 is formed in the cover plate 2I2A and incorresponding portions of the cover plate or casting 2I2 there areprovided openings 231. Within the inner portions of the groove 236 andthe annular opening 231 are inserted the bushing rings 210 and 21!,forming bearing means for the ring 235.

As in the case of the embodiment previously described, ring or sleeve235 is provided with a rectangular, longitudinally extending, radialslot or opening 238, to accommodate the radial vane 221. The sleeve 235is provided with a hollow interior chamber 253 which is longitudinallyclosed at one side of the opening 238 by means of the wall 258, but isopen for the admission of fluid at its opposite end as at 259 adjacentthe forward face of the vane 221 which is provided with the scoop-likerecesses 229. The sleeve 235 is preferably made in two principal parts,the

outer part consisting of the cylindrical wall 215, and the other partcomprising the inner wall portion 211 together with the end wall fitsinto the groove 236.

As best shown in Figs. 12 and 13 of the draw- -ings, the inner member ofthe ring 235 is provided with an annular projection 219 having acircular series of openings 28. therein; Beyond. the openings 2 thisinner member of the sleeve 235 is provided with curved vanes 215. Thewall 216 of the sleeve 235 where it projects into the outlet chamber 255in the head casting 2I2'is provided with an annular series of slots 254,through which the liquid is radially discharged to obtain a centrifugalaction within the outlet chamber 255. This centrifugal outlet chamber issimilar in most respects with the outlet chambers and I55 of theembodiments previously described, and is provided with outletconnections (not shown) similar to those indicated at 55 and I55 in theearlier figures of the drawing. At the outlet end of the sleeve 235,there is disposed an annular cover plate'282, preferably made of sheetmetal and of an arcuate section. This plate is applied to the curvededges of the blades 215 and serves to smoothly direct theliquid betweenthe blades and through the slots 254.

The lower portion of the chamber 2I3 is provided with a recess 24lwithin which there is disposed a hinged sealing element 240, pivotallymounted as at 240A 'and constructed and arranged to operate in the samemanner as the seal I40 in the embodiment previously described. Aclean-out opening is provided at 2MB.

Where the hub 225 comes in rolling contact with the surface of the innerwall 211 of the sleeve 253, there is provided the novel pressuredifferential and centrifugal sealing installation 242. As best seen inFigs. 11 and 15, the sealing element 242 comprises a flexible andsomewhat resilient strip formed with crimped or undulating portions 242Aat intervals around the structure, each adapted to be received withinone of p the narrow-mouthed recesses 225A in the hub 225. As shown inFig. 15, at all points around the hub 225 remote from the ever-changinglines of contact at 243, the sealing strip 242 stands somewhat away fromthe surface of the hub, leaving a space 242B between these elements.Similarly, a space 242C occurs between the looped or crimped portions242A of the sealing element and the surfaces of the recesses 225A.However, adjacent the point of rolling contact 243, the ring 235 pressesthe sealing element 242 closer to the surface of the hub. Thus, anyfluid beneath the strip 242 within the spaces 242B and 242C is squeezedor pressed along from one pocket or recess to the other, thus supplyinga sealing pressure passing into the low pressure region. By this means,sealing under pressure is assured, as well as the natural centrifugalsealing effect resulting fro-m the rotation of the impeller.

In order to prevent wearing and the possibility of noisy contact betweenthe forward and rear faces of the vane 221 and the walls of the opening238 adjacent the opposite ends 258 and 259 of the sleeve chamber 253, amechanical connection is provided between the vane 221 and the sleeve235. This connection is best shown in Figs. 10, 12, and 14 of thedrawings, and comprises a circular stud or plug 290 at one end of whichis formed a longitudinal key portion 29L The circular part 290 isreceived within a similarly shaped recess 292 formed in a solid portion293 of the sleeve 235 where one or more of the 218 which outlet openings280 are omitted, and of course adjacent the opening 258 through whichthe vane 221 passes. I A longitudinal groove 294 is formed in one edgeof the vane 221 to receive the key portion 291 of the connectingelement. This groove or slot 294 is necessarily of greater length thanthe key 291 in order to provide for reciprocating movement due to theeccentricity of the sleeve 235 with respect to the impeller230 and itsvane 229.

Although the mechanical drivi-ng means just described are featured inthe embodiments of the.

invention disclosed in the present specification, these means arecomplementary to and serve to augment the fluid pressure driving forceasserted on the sleeve by virtue of thehydraulic phenomenon more fullyset forth and claimed in my copending application Serial No. 758,871,filed July 3, 1947. Due to the construction of the pump and therelationship of its operating parts, the velocity of the fluid passingthrough the displacement portion of the pump is somewhat greater thanthat of the sleeve; thus, there is an absorption of energy, under mostconditions of operation, suflicient to carry the sleeve around its orbitwithout continually being forced by the vane through the key member 290,291. Thus, even when the mechanical drive means are employed, excessivewear on those parts is prevented.

At 295 in Fig. there is shown a partition which separates the activespace 253 of the interior of the sleeve 235 from a dead space 296 beyondthe partition. The sleeve is not made solid at this point since thiswould unnecessarily add to the weight of the pump. The liquid moveslaterally through the space 253 due to differences in pressure at theseveral points along its course through the outlet chamber and thecentral displacement chamber. However, in the embodiment of the sleeveillustrated in Figs. 12 and 13, a helical partition 291 is formed uponthe inner section 211 of the sleeve and this partition, together withthe inner wall 211 and the outer wall 216, forms a gradually narrowingchamber from which the liquid is "squeezed through the openings 280 bymeans of the helical wall 291. Rearwardly of the wall or partition 291there is an expanding dead space 298. By means of this helical partitionthere is provided in effect a screw conveyor for the fluid which actsfurther to displace the fluid toward the delivery point.

In Fig. 16 there is shown a development of the sleeve chamber, thedelivery openings with their blades, arid the expanding outlet chamber.It will be seen from this diagram that the contraction of the sleevechamber 253 is substantially comparable to the expansion of thecentrifugal outlet chamber 255. During the transfer of the fluid throughthis portion of the pump, energy is absorbed which may be sufficlent tocarry the sleeve through its orbit. Thus, the load on the pivot key 290,291 may be partially or wholly relieved.

In Figs. 17-21 inclusive there is illustrated another embodiment ofeccentric sleeve which is designated generally by the reference numeral335. For the most part, this sleeve is constructed s milarly tothesleeve 235 and similar reference characters will be employed. Forexample, the outer annular wall is shown at 315, the inner casting ofthe sleeve is indicated at 311, the helical blade or partition isdesignated 391, the opening for the impeller vane is shown at 333, thede- 10 livery passageway through the sleeve at 353, the dead space at398, and the pivot-key element at 390 391. is constructed differentlyfrom the previous embodiment and the new arrangement is probably bestshown in Fig. 17. The sleeve, at this end, is provided with an end wall400 which is relieved at intervals by the radially outwardly flaredopenings 4111. Upon one side of each of these openings there areprovided axially extending blades, fins, or vanes 4112 which extend forthe full width of the opening and are arcuately curved upon their innersides as at 403. A sheet metal cover (not shown) may be provided in thiscase similar to the one indicated at 282 in Figs. 12 and 13 of thedrawings. Upon the opposite side of each of the openings 401 there areprovided the narrower blades or vanes404 which are curved at their endsto conform to the cover plate and the configuration of the outletchamber, but are cut oil as at 4115 at about half the width of the otherblades 402. At one point around the end of the sleeve, the opening 401is omitted to make room for the pivot key element 399, 391, as clearlyshown in Figs. 17 and 21.

A still further modification of the invention is illustrated in Figures22-26 of the drawings, the chief diflerences in this arrangement overthe others previously described being a variation in the form of thesealing devices, changes in the discharge means of the rotary sleeve,and novel interlocking arrangements between the driving vane of theimpeller and the eccentric rotating hollow ring or sleeve. These andother changes in the construction and arrangement of the pump will bedescribed in detail.

As indicated in Figure 26 of the drawings, this form of the pumpcomprises a pump casing 410 provided with the feet or pedestals 422 anda vertically disposed outlet connection 455 to which a discharge pipe4515A is attached. The inlet connection 451, as in the case of theearlier described embodiments, is disposed axially ofthe driving shaft415, as will be readily perceived by inspection of Figures 22 and 23 ofthe drawings.

In these two figures it will be seen that the casing designatedgenerally by the numeral 419 comprises a main body portion 411 and acover plate 412, these members enclosing a substantially cylindricalworking chamber 413 and a discharge chamber 455. A lining ring 414 isdisposed within the chamber 413, this ring providing a smooth interiorsurface or inner wall 439 against which the rotating impeller is adaptedto slide, and also enabling the provision of an enlarged housingfacilitating the boring of the bushing seats or grooves in the casingmember 411, between the chambers 413 and 455.

The drive shaft 415 enters the pump casing through an opening 415 in thebody portion 411, which opening is provided with a bushing and stuflingbox assembly 423.

The drive shaft 415 is provided with an enlarged hollow hub portion 425,the interior 4511 of which opens endwise toward the axial intakeconnection 451 to which the inlet pipe 451A is fitted. The outer end ofthe hub 425 is narrowed as at 425A and is surrounded by a crimp ring42513 which isenclosed within the flanged ring 4250, which arrangementprovides a journal bearing for the hub at the cover plate end of thecasing.

The impeller vane is designated by the numeral 421 and is generallysimilar to the vane 321 of the embodiment illustrated in Figures 10 and11 of the drawings, being formed with a hollowed The outlet end of thesleeve, however,

out discharge portion 46l which extends approximately radially of thevane and opens outwardly through the rearward surface of the vane. Theforward surface, according to the direction of rotation of the impeller,is provided with the scoop portions 429 similar to the arrangement shownin Figures and 11. The base of the vane 421 is provided with shoulderedportions providing an inter-lock 428 with similar shouldered portionscut in the hollow hub 425. The vane and the hub thus are rigidlyconnected together to form an impeller unit assembly designatedgenerally by the numeral 430.

The eccentric hollow ring or sleeve is denoted generally by thereference numeral 435, and is shown in some detail in Figure 24 of thedrawings as well as in Figures 22 and 23. The inner portion of thesleeve comprises a substantially annular member 411 having lateralflanges 411A and a shouldered outlet portion 419 providing a restrictedseries of outlet orifices 480. The inner portion 411 of the sleeve isenclosed by an outer ring 416, one margin 416A of which covers theorifice portion 480 of the sleeve and the opposite edge 4163 projectsaxially beyond the inner portion 411 and is journaled within the annulargroove 436 of the cover plate 412. A bushing or bearing ring 436Asurrounds this portion of the sleeve. The opposite end of the sleevebears in a bushing 431 and a sealing ring 431A is disposed within agroove in the casing upon the inner side of the rotating sleeve at thisend of the device.

The lining ring 4l4 within the housing H3 is provided with a sealingflap 440 which seats in a recess 44! formed in the inner surface of thering 414. The seal element 440 is of resilient construction and one edgeis received within a slit 441A formed in the ring M4, The seal 440 formsa similar function, and in substantially the same manner, as the hingedsealing member 240 shown in Figure 11 of the drawings. A clean-outopening 44 IB is also provided at this point in the easing 41 I.

The rolling contact seal element 442 is wrapped around the outer surfaceof the hub 425 and is designed to perform the same function as the seal242 shown in Figure 11.

The seal 442 comprises a sheet of metal, plastic, or other suitablematerial, and is of a crimped construction having overlapping foldsprovided by a zlg-Zag formation of the sheet around the surface of thehub, the ends 444 and 445 of the seal are inserted in slits formed inthe side walls of the vane 421 as clearly shown in Figure 22 of thedrawings. The superposed folds or laminations of the sealing member whenrotating in rolling contact with theinner wall 411 of the sleeve 435will pass through alternating high and low pressure regions and thecircumferential spaces behind the seal and under the overlapping foldswill absorb some of the pressure of the fluid substantially greater thanthe minimum. It is evident, therefore, that this pressure differentialwill tend to pull portions of the seal into the low pressure chamber.This condition is similar to that produced in the embodiment shown in,Figures 11 and 15 of the drawings, and it will be readily seen how theseal produces the described cushioning and sealing effect.

The vane 421, as in the earlier embodiments, passes through an elongatedopening 452 in the sleeve 435, and although the back pressure of the 12driven by contact with the forward edge of the vane. As shown in Figure24 of the drawings the side portions of the vane 421 are of dove-tailformation'as indicated at 421A, and fit within the similarly formedundercut portions 435A of the sleeve.

The end portion 419 of the inner part of the sleeve which cooperateswith the edge 416A of the outer part to form the restricted dischargeopenings 480 are provided with streamlined partitions 48! which arecurved so as to discharge the fluid through the outlet passageways 480between these partitions in a generally tangential direction within theexhaust or outlet chamber 455 formed in the casing 4H and communicatingwith the outlet connection 456. This gives a centrifugal effectcomparable to that attained by the discharge structure shown at theright hand side of Figure 10 and in Figure 12 of the previousembodiment. It will be noted that the curvature of the discharge slotsor orifices 480 is in a direction away from the direction of rotation ofthe rotor so that the reaction of the discharged fluid aids the rotaryeffort.

Reviewing the construction and operation of this pump, it will -be seenthat first of all, the liquid is thrown centrifugally through the hollowvane 21-421 to the outer portions of the working chamber. Then theliquid is moved through the casing mainly by displacement until itreaches the outlet or exhaust chamber 55-455, whereupon a finalcentrifugal stage is efiected.

It is well known that practically every rotary pump can be convertedinto a liquid motor by reversing the action thereof and thus the liquidmay be supplied under pressure and the power taken off the rotor shaftinstead of applying driving power thereto. An important feature of thepresent arrangement lies in that a compressible medium such as air orsteam can be used as the driving means in converting the present pump toa motor. In the case of steam the supply enters the primary stage,namely the displacement chamber, and may be allowed to expand into thesecondary stage, namely the turbine section. In this way, several unitsmay be hooked up in pairs with the steam finally entering the condenser.

Various changes and modifications may be made in the embodimentsillustrated and described herein without departing from the scope of theinvention as defined in the following claims.

Having thus described the invention what is claimed as new and desiredto be secured by Letters Patent is:

1. A rotary pump for transferring substantially incompressible liquids,comprising, in combination, a stationary casing having :a smooth,uninterrupted, inner cylindrical wal1 enclosing a working chamber, animpeller member rotatably mounted within said casing and co-axiallytherewith, said impeller member comprising a central substantiallycylindrical hub forming a substantially annular working space of uniformradius between the hub and the inner circumferential wall of saidcasing, an eccentrically disposed annular sleeve surrounding saidimpeller hub, said sleeve being internally tangent to said hub andexternally tangent to said inner wall of the casing and free to rotateabout its own center with the points of tangency substantially fixed atdiametrically opposite sides of the axis of the casing, whereby saidworking space is divided into two chambers the cross sections of whichcomprise complementary oppositely facing interlocking lunes, a radiallyextending vane carried by said hub and constituting the eflective movingpart of the impeller member, said vane passing through a slot in saidsleeve with its outer end having a continuous sliding fit with the innerperipheral wall of the casing, whereby the rotaportions, means forventing fluid from said discharging portions, and means for driving theimpeller member, said annular sleeve being hollow, and one among thefluid supplying and fluid venting means comprising a passageway throughsaid vane and the other among said fluid venting and fluid supplyingmeans compressing a passageway through said hollow sleeve.

2. A rotary pump for transferring substantially incompressible liquids,comprising, in combination, a substantially cylindrical casing, animpeller member rotatably mounted within said casing and co-axiallytherewith, said impeller member comprising a centralsubstantially'cylindrical hub forming a substantially annular workingspace of uniform radius between the hub and the inner circumferentialwall of said casing, an eccentrically disposed annular sleevesurrounding said impeller hub, said sleeve being internally tangent tosaid hub and externally tangent to said inner wall of the casing andfree to rotate about its own center with the points of tangencysubstantially flxed at diametrically opposite sides of the axis of thecasing, whereby said working space is divided into two chambers thecross sections of which comprise complementary oppositely facinginterlocking lunes. a radially extending vane carried by said hub andconstitut ng the eiiective moving part of the impeller member, said vanepassing through a slot in said sleeve with its outer end having asliding fit with the inner peripheral wall of the casing, whereby therotation of the impeller member and the sleeve causes a progressive andalternate division of the respective lune-shaped chambers intosuccessively waxing and waning fluid receiving and fluid dischargingportions, the discharging portions in the case of both chambers being inadvance of said vane and the receiving portions rearward thereofconsidering the direction of rotation, means for supplying fluid to saidrespective receiving portions of the chamber, means on said sleeve forventing said fluid from both of said discharge port ons, a fluid outletpassageway for receiving the fiuid from said last named means, and meansfor driving said impeller member, the said means on said sleeve being soconstructed and arranged as to have unobstructed access to said portionsat all times except momentarily at instants when one of said portions ofa lune-shaped chamber is at maximum capacity and the other at zerocapacity.

3. A rotary pump comprising, in combination, a substantially cylindricalcasing, an impeller member rotatablymounted within said casing andco-axially therewith, said impeller member comprising a centralsubstantially cylindrical hub forming a substantially annular workingspace of uniform radius between the hub and the inner circumferentialwall of said casing, an eccentrically disposed annular sleevesurrounding said impeller hub, said sleeve being internally tangent tosaid hub and externally tangent to said inner wall of the casing, andfree to rotate about its own center with the points of tangencysubstantially fixed at diametrically opposite sides of the axis of thecasing, whereby said working space is divided into two chambers thecross sections of which comprise complementary oppositely facinginterlocking lunes, a radially extending vane carried by said hub andconstituting the effective moving part of the impeller member, said vanepassing through a slot in said sleeve with its'outer end having asliding fit with the inner peripheral wall of the casing, whereby therotation of the impeller member and the sleeve causes a progressive andalternate division of the respective lune-shaped chambers intosuccessively waxing and waning fluid receiving and fluid dischargingportions, the discharging portions in the case of both chambers being inadvance of said vane and the receiving portions rearward thereofconsidering the direction of rotation, means for supplying fluid to saidrespective receiving portions of the chambers, said annular sleeve beingprovided with a longitudinal passageway open to both chambers on theforward side of said vane, an outlet chamber in said casing continuallin communication with said passageway, and means for driving saidimpeller.

4. A rotary pump comprising, in combination, a substantially cylindricalcasing, an impeller member rotatably mounted within said casing andco-axially therewith, said impeller member comprising a centralsubstantially cylindrical hub forming a substantially annular workingspace of uniform radius between the hub and the inner circumferentialwall of said casing, an eccentrically disposed annular sleevesurrounding said impeller hub, said sleeve being internall tangent tosaid hub and externally tangent to said inner wall of the casing andfree to rotate about its own center with the points of tangencsubstantially fixed at diametrically opposite sides of the axis of thecasing, whereby said working space is divided into two chambers thecross sections of which comprise complementary oppositely facinginterlocking lunes, a radially extending vane carried by said hub andconstituting the effective moving part of the impeller member. said vanepassing through a slot in said sleeve with its outer end having asliding fit with the inner peripheral wall of the casing, whereby therotation of the impeller member and the sleeve causes a progressive andalternate division of the respective luneshaped chambers intosuccessively waxing and waning fluid receiving and fluid dischargingportions, the discharging portions in the case of both chambers being inadvance of said vane and the receiving portions rearward thereofconsidering the direction of rotation. means for supplying fluid to saidrespective receiving portions of the chambers, said annular sleeve beinghollow and having openings leading into the interior thereof from bothchambers adjacent the forward face of said vane, an outlet chamber insaid casing, means providing continuous communication between theinterior of said sleeve and said outlet chamber, and means for drivingsaid impeller member.

5. A rotary pump comprising, in comb nation, a substantially cylindricalcasing, an impeller member rotatably mounted within said casing andco-axially therewith, said impeller member comprising a centralsubstantially cylindrical hub forming a substantially annular workingspace of uniform radius between the hub and the inner circumferentialwall of said casing, an eccentrical- 1y disposed annular sleevesurrounding said impeller hub, said sleeve being internally tangent tosaid hub and externally tangent to said inner wall of the casing andfree to rotate about its own center with the points of tangencysubstantially fixed at diametrically opposite sides of the axis of thecasing, whereby said working space is divided into two chambers thecross sections of which comprise complementary oppositely facinginterlocking lunes, a radially extending vane carried by said hub andconstituting the effective moving part of the impeller member, said vanepassing through a slot in said sleeve with its outer end having asliding fit with the inner peripheral wall of the casing, whereby therotation of the impeller member and the sleeve causes a progressive andalternate division of the respective luneshaped chambers intosuccessively waxing and waning fluid receiving and fluid dischargingportions, the discharging portions in the case of both chambers being inadvance of said vane and the receiving portions rearward thereofconsidering the direction of rotation, both the hub and vane of theimpeller member being hollow and the latter part thereof provided withopenings in its trailing wall which faces the receiving chambers, thusproviding means for delivering fluid centrifugally to the respectivereceiving portions of the chamber, said annular sleeve also being hollowand having openings leading into the interior thereof from both chambersadjacent the forward face of said vane, an outlet chamber in saidcasing, means providing continuous communication between the interior ofsaid sleeve and said outlet chamber, and means for driving said impellermember.

6. A rotary pump comprising, in combination, a substantially cylindricalcasing, an impeller member rotatably mounted within said casing andco-axially therewith, said impeller member comprising a centralsubstantially cylindrical hub forming a substantially annular workingspace of uniform radius between the hub and the inner circumferentialwall of said casing, an eccentricallly disposed annular sleevesurrounding said impeller hub, said sleeve being internally tangent tosaid hub and externally tangent to said inner wall of the casing andfree to rotate about its own center with the points of tangencysubstantially fixed at diametrically opposite sides of the axis of thecasing, whereby said working space is divided into two chambers thecross sections of which comprise complementary oppositely facinginterlocking lunes, a radially extending vane carried by said hub andconstituting the effective moving part of the impeller member, said vanepassing through a slot in said sleeve with its outer end having asliding fit with the inner peripheral wall of the casing, whereby therotation of the impeller member and the sleeve causes a progressive andalternate division of the respective lune-shaped chambers intosuccessively waxing and waning fluid receiving and fluid dis-- chargingportions, the discharging portions in the case of both chambers being inadvance of said vane and the receiving portions rearward thereofconsidering the direction of rotation, means for supplying fluid to saidrespective receiving portions of the chambers, said annular said casingcontinually in communication with said passageway, the construction andarrangement being such that the fluid is given a rotary motion in theoutlet chamber and discharged tangentially therefrom, and means fordriving said impeller member.

7. A rotary pump comprising, in combination, a substantially cylindricalcasing, an impeller member rotatably mounted within said casing andco-axlally therewith, said impeller member comprising a centralsubstantially cylindrical hub forming a substantially annular workingspace of uniform radius between the hub and the inner circumferentialwall of said casing, an eccentrically disposed annular sleevesurrounding said impeller hub, said sleeve being internally tangent tosaid hub and externally tangent to said inner wall of the casing andfree to rotate about its own center with the points of tangencysubstantially fixed at diametrically opposite sides of the axis of thecasing, whereby said working space is divided into two chambers thecross sections of which comprise complementary oppositely facinginterlocking lunes, a radially extending vane carried by said hub andconstituting the eiiective moving part of the impeller member, said vanepassing through a slot in said sleeve with'its outer end having asliding fit with the inner peripheral wall of the casing, whereby therotation of the impeller member and the sleeve causes a progressive andalternate division of the respective luneshaped chambers intosuccessively waxing and waning fluid receiving and fluid dischargingportions, the discharging portions in the case of both chambers being inadvance of said vane and the receiving portions rearward thereofconsidering the direction of rotation, sealing means at the point ofsliding contact between the sleeve and sleeve being provided with alongitudinal pasthe casing wall at one of said fixed points of tangency,a sealing annulus on one of the contacting elements at the point ofcombined sliding and rolling contact at the other fixed point oftangency, means for supplying fluid to and venting it from saidrespective portions of the chambers, and means for driving said impellermember.

8. A rotary pump comprising, in combination, a substantially cylindricalcasing, an impeller member rotatably mounted within said casing andco-axially therewith, said impeller member comprising a centralsubstantially cylindrical hub forming a substantially annular'workingspace of uniform radius between the hub and the inner circumferentialwall of said casing, an eccentrically disposed annular sleevesurrounding said impeller hub, said sleeve being internally tangent tosaid hub and externally tangent to said inner wall of the casing andfree to rotate about its own center with the points of tangencysubstantially fixed at diametrically opposite sides of the axis of thecasing, whereby said working space is divided into two chambers thecross sections of which comprise complementary oppositely facinginterlocking lunes, a radially extending vane carried by said hub andconstituting the effective moving part of the impeller member, said vanepassing through a slot in said sleeve with its outer .end having asliding fit with the inner peripheral wall of the casing, whereby therotation of the impeller member and the sleeve causes a progressive andalternate division of the respective luneshaped chambers intosuccessively waxing and waning fluid receiving and fluid dischargingportions, the discharging portions in the case of both chambers being inadvance of said vane and some the receiving portions rearward thereofconsidering the direction of rotation, sealing means at the point ofsliding contact between the sleeve and the casing wall at one of saidfixed points of tangency, an annulus of sealing composition wrappedaround said hub and providing sealing means at the point of combinedsliding and rolling contact at the other fixed point of tangency. meansfor supplying fluid to and venting it from said respective portions ofthe chambers, and means for driving said impeller member.

9. A rotary pump comprising, in combination, a substantially cylindricalcasing, an impeller member rotatably mounted within said casin andco-axially therewith, said impeller member comprising a centralsubstantially cylindrical hub forming a substantially annular workingspace of uniform radius between the hub and the inner circumferentialwall of said casing, an eccentrically disposed annular sleevesurrounding said impeller hub, said sleeve being internally tangent tosaid hub and externally tangent to said inner wall of the casing andfree to rotate about its own center with the points of tangencysubstantially fixed at diametrically opposite sides of the axis of thecasing, whereby said working space is divided into two chambers thecross sections of which comprise complementary oppositely facinginterlocking lunes, a radially extending vane carried by said hub andconstituting the effective moving part of the impeller member, said vanepassing through a slot in said sleeve with its outer end having asliding fit with the inner peripheral wall of the casing, whereby therotation of the impeller member and the sleeve causes a progressive andalternate division of the respective luneshaped chambers intosuccessively waxing and waning fluid receiving and fluid dischargingportions, the discharging portions in the case of both chambers being inadvance of said vane and the receiving portions rearward thereofconsidering the direction of rotation, means for independently supplyingfluid to the fluid receiving portions, said annular sleeve being hollowproviding an annular chamber, said chamber opening toward the forwardface of the vane to receive fluid from said discharge portions, and anopening in one end of said sleeve for discharging fluid from saidannular chamber axially outwardly of the workin chamber, and means fordriving said impeller member. a

10. A rotary pump comprising, in combination, a substantiallycylindrical casing, an impeller member rotatably mounted within saidcasing and co-axially therewith, said impeller member comprising acentral substantially cylindrical hub forming a substantially annularworking space of uniform radius between the hub and the innercircumferential wall of said casing, an eccentrically disposed annularsleeve surrounding said impeller hub,.said sleeve being internallytangent to said hub and externally tangent to said inner wall of thecasing and free to rotate about its own center with the points oftangency substantially fixed at diametrically opposite sides of the axisof the casing, whereby said working space is divided into two chambersthe cross sections of which comprise complementary oppositely facinginterlocking lunes, a radially extending vane carried by said hub andconstituting the effective. moving part of the impeller member, saidvane passing through a slot in said sleeve with its outer end having asliding fit with the inner peripheral wall of the casing. whereby therotation of the impeller member and the sleeve causes a progressive l8and alternate division of the respective luneshaped chambers intosuccessively waxing and waning fluid receiving and fluid dischargingportions, the discharging portions in the case of both chambers being inadvance of said v'ane and the receiving portions rearward thereofconsiderin the direction of rotation, means for independently supplyingfluid to the fluid receiving portions, said annular sleeve being hollowproviding an annular chamber, said chamber opening toward the forwardface of the vane to receive fluid from said discharge portions, anexhaust chamber disposed at one end of said working chamber, one end ofsaid sleeve projecting through a slot in the casing communicating withsaid exhaust chamber, and a plurality of openings in said end of thesleeve for discharging fluid into said exhaust chamber, and means fordriving said impeller.

11. The pump according to claim 9 in which there is provided a radiallyprojecting helically formed blade in said annular chamber functioning asa screw conveyor for transferring the fluid endwise thereof and throughsaid discharge openings.

12. The pump according to claim 10 in which a series of vanes areprovided on said end of the sleeve for swirling the fluid as it isdischarged into said exhaust chamber.

13. The pump according to claim 10 in which said exhaust chamber is ofexpanding volume toward a tangential outlet, and a series of vanes areprovided on said end of said sleeve for swirling the fluid as it isdischarged into said exhaust chamber and attaining a final centrifugalpumping effect.

14. The pump according to claim 10 in which there is provided a radiallyprojecting helically formed blade in said annular chamber functioning asa screw conveyor for transferring the fluid endwise thereof and throughsaid discharge opening, and wherein said exhaust chamber is of expandingvolume toward a tangential outlet, and a series of vanes is provided onsaid end of the sleeve for swirling the fluid as it is discharged intosaid exhaust chamber and attaining a final centrifugal pumping effect.

15. A rotary pump comprising, in combination, a substantiallycylindrical casing, an impeller member rotatably mounted within saidcasing and co-axially therewith, said impeller member comw fixed atdiametrically opposite sides of the axis of the casing, whereby saidworking space is divided into two chambers the cross sections of I whichcomprise complementary oppositely facing interlocking lunes, a radiallyextending vane car- .5 ried by said hub and constituting the effectivemoving part of the impeller member, said vane passing through a slot insaid sleeve with its outer end having a sliding flt with the innerperipheral wall of the casing, whereby the rotation of the 7 impellermember and the sleeve causes a progressive and alternate division of therespective luneshaped chambers into successively waxing and waning fluidreceiving and fluid discharging portions, the discharging portions inthe case of both chambers being in advance of said vane and thereceiving portions rearward thereof considering the direction ofrotation, means for independently supplying fluid to the fluid receivingportions, said annular sleeve being hollow providing an annular chamber,said chamber opening toward the forward face of the vane to receivefluid from said discharge portions, an exhaust chamber disposed at oneend of said working chamber, one end of said sleeve projecting through aslot in the casing communicating with said exhaust chamber, and aplurality of orifices opening radially outwardly at said end of thesleeve for discharging fluid into said exhaust chamber and setting up aswirl therein, a tangential outlet for said exhaust chamber, and meansfor driving said impeller.

16. A rotary pump comprising, in combination, a substantiallycylindrical casing, an impeller member rotatably mounted within saidcasing and co-axially therewith, said impeller member comprising acentral substantially cylindrical hub forming a substantially annularworking space of uniform radius between the hub and the innercircumferential wall of said casing, an eccentrically disposed annularsleeve surrounding said impeller hub, said sleeve being internallytangent to said hub and externally tangent to said inner wall of thecasing and free to rotate about its own center with the points oftangency substantially flxed at diametrically opposite sides of the axisof the casing, whereby said working space is divided into two chambersthe cross sections of which comprise complementary oppositely facinginterlocking lunes, a radially extending vane carried by said hub andconstituting the effective moving part of the impeller member, said vanepassing through a slot in said sleeve with its outer end having asliding fit with the inner peripheral wall of the casing, whereby therotation of the impeller member and the sleeve causes a progressive andalternate division of the respective lune-shaped chambers intosuccessively waxing and waning fluid receiving and fluid dischargingportions, the discharging portions in the case of both chambers being inadvance of said vane and the receiving portions rearward thereofconsidering the direction of rotation, a pin and slot pivotal connectionbetween said vane and said sleeve, means for venting fluid from saiddischarging portions, and means for driving the impeller member.

17. A rotary pump comprising, in combination, a substantiallycylindrical casing, an impeller member rotatably mounted within saidcasing and co-axially therewith, said impeller member comprising acentral substantially cylindrical hub forming a substantially annularworking space of uniform radius between the hub and the innercircumferential wall of said casing, an eccentrically disposed annularsleeve surrounding said impeller hub, said sleeve being internallytangent to said hub and externally tangent to said inner wall of thecasing and free to rotate about its own center with the points oftangency substantially fixed at diametrically opposite sides of the axisof the casing, whereby said working space is divided into two chambersthe cross sections of which comprise complementary oppositely facinginterlocking lunes, a radially extending vane carried by said hub andconstituting the effective moving part of the impeller member, said vanepassing through a slot in said sleeve with its outer end having asliding fit with the inner peripheral wall oi the casing, whereby therotation of the impeller member and the sleeve cause a progressive andalternate division of the respective luneshaped chambers intosuccessively waxing and waning fluid receiving and fluid dischargingportions, the discharging portions in the case of both chambers being inadvance of said vane and the receiving portions rearward thereofconsidering the direction of rotation, a groove in the end wall of saidvane, a circular opening in the wall of the slot in the sleeve throughwhich the vane passes, a key having a circular part rotatably receivedwithin said opening and a squared part slidably received in said groove,said key adapted to take any stresses between the vane and the sleevethus relieving the portions of said members adjacent said slot fromwear.

18. A rotary pump comprising, in combination, a substantiallycylindrical casing, an impeller member rotatably mounted within saidcasing and co-axially therewith, said impeller member comprising acentral substantially cylindrical hub forming a substantially annularworking space of uniform radius between the hub and the innercircumferential wall of said casing, an eccentrically disposedannularsieeve surrounding said impeller hub, said sleeve beinginternally tangent to said hub and externally tangent to said inner wallof the casing and free to rotate about its own center with the points oftangency substantially fixed at diametrically opp site sides of the axisof the casing, whereby said working space is divided-into two chambersthe cross sections of which comprise complementary oppositely facinginterlocking lunes, a radially extending vane carried by said hub andconstituting the effective moving part of the impeller member, said vanepassing through a slot in said sleeve with its outer end having asliding fit with the inner peripheral wall of the casing, whereby therotation of the impeller member and the sleeve cause a progressive andalternate division of the respective lune-shaped chambers intosuccessively waxing and waning fluid receiving and fluid dischargingportions, the discharging portions in the case of both chambers being inadvance of said vane and the receiving portions rearward thereofconsidering the direction of rotation, means for independently supplyingfluid to the fluid receiving portions, means for venting fluid from saiddischarging portions, and means for driving the impeller member, asealing element extending axially of said working chamber at the pointof external tangency of the sleeve with the outer wall of the chamber,and a sealing member between said hub and the internal surface of saidsleeve to seal off the successive points of tangency of the hub withsaid sleeveduring their rolling contact.

19. A rotary pump of the class described comprising a casing having aworking chamber therein, a cylindrical wall surface therein and animpeller portion having a cylindrical surface, the wall and impellerportion being of different diameters, mounted eccentrically with respectto each other, and said surfaces being tangent to each other and inrolling contact, the line of tangency bounding two fluid chambers underdifferent pressures, a sealing member covering one of said surfaces, andmeans admitting high pressure fiuidbehind said sealing member to aid inmaintaining the seal.

20. A rotary pump of the class described comprising a casing having aworking chambi therein, a cylindrical wall surface therein and animpeller portion having a cylindrical surface, the wall and impellerportion being of different diainthe sealing member is applied, thesealing member being crimped to form folds inserted in said slots toretain the member in position.

21. A rotary pump of the class described comprising a casing having aworking chamber therein, a cylindrical wall surface therein and animpeller portion having a cylindrical surface the wall and impellerportion being of different dia'nieters, mounted eccentrically withrespect to each other, and said surfaces being tangent to each other andin rolling contact, the line of tangency bounding two fluid chambersunder different pressures, a sealing member covering one of saidsurfaces, the sealing member comprising sheet material crimped to form aseries of overlapping folds, the construction and arrangement permittingadmission of high pressure fluid within and behind said folds, wherebysaid sealing member is cushioned to better perform its function duringthe rolling contact of the tangent surfaces.

22. A rotary pump of the class described comprising a casing having aworking chamber therein, a cylindrical wall surface therein and animpeller portion having a cylindrical surface, the wall and impellerportion being of different diameters, mounted eccentrically with respectto each other, and said surfaces being tangent to each other and inrolling contact, the line of tangency bounding two fluid chambers underdifferent pressures, a sealing member covering one of said surfaces, andmeans admitting high pressure fluid behind said sealing member to aid inmaintaining the seal, a series of circumferentially spaced axiallyextending pockets in the surface to which the sealing member is applied,the pockets having restricted mouths, and bights formed in said sealingmember and loosely retained in the slots.

23. A rotary pump comprising, in combination,

a substantially cylindrical casing, an annular liner ring fixed withinsaid casing and providing a pcripheral inner wall for the casing, animpeller member rotatably mounted within said casing and co-axiallytherewith, said impeller member comprising a central substantiallycylindrical hub forming a substantially annular working space of uniformradius between the hub and the inner circumferential wall of saidcasing, an eccentrically disposed annular sleeve surrounding saidimpeller hub and rotatably received within annular grooves provided inthe end walls of the casing, said sleeve being internally tangent tosaid hub and externally tangent to said inner wall of the casing andfree to rotate about its own center with the points of tangencysubstantially fixed at diametrically oppositesidesof th -ax s of thecasing, whereby said working space'is divided into two chambers thecross sections of which comprise complementary oppositely facinginterlocking lunes, a radially extending vane caracne-11s progressiveand alternate division of the respective lune-shaped chambers intosuccessively waxing and'waning fluid receiving and fluid dischargingportions, the discharging portions in the case' of both chambers beingin advance of said vane and the receiving portions rearward thereofconsidering the direction of rotation, a sealing member carried by saidliner ring at the point of sliding contact between the sleeve and thecasing wall at one of said fixed points of tangency, means for supplyingfluid to and venting it from said respective portions of the chambers,and means for driving said impeller member.

24. A rotary pump comprising, in combination, a substantiallycylindrical casing, an impeller member rotatably mounted within saidcasing and co-axially therewith, said impeller member comprising acentral substantially cylindrical hub forminga'substantially annularworking space of uniform radius between the hub and the innercircumferential wall of said casing, an eccentrically disposed annularsleeve surrounding said impeller hub, said sleeve being internallytangent to said hub and externally tangent to said inner wall of thecasing and free to rotate about its own center with the points oftangency substantially fixed at diametrically opposite sides of the axisof the casing, whereby said working space is divided into two chambersthe cross sections of which comprise complementary oppositely facinginterlocking lunes, a radially extending vane carriedvby said hub andconstituting the effective moving part of the impeller member, said vanepassing through a slot in said sleeve, said slot and said vane beingprovided with interlocking shoulder portions providing a drivingconnection between them, the outer end of said vane having a sliding fltwith the inner peripheral wall of the casing, whereby the rotation ofthe impeller member and the sleeve causes a progressive and alternatedivision of the respective luneshaped chambers into successively waxinand waning fluid receiving and fluid discharging portions, thedischarging portions in the case of both chambers being in advance ofsaid vane and the receiving portions rearward thereof considering thedirection of rotation, means for independently supplying fluid to thefluid receiving portions, said annular sleeve being hollow providing anannular chamber, said chamber opening toward the forward face of thevane to receive fluid from said discharge portions, and an opening inone end of said sleeve for discharging fluid from said annular chamberaxially outwardly of the working chamber, and means for driving saidimpeller member.

25. A rotary pump comprising, in combination, a substantiallycylindrical cas n an impeller member rotatably mounted within saidcasing and co-axially therewith, said impeller member comprising acentral substantially cylindrical hub forming a substantially annularworking space of uniform radius between the hub and the innercircumferential wall of said casing, an eccentrically disposed annularsleeve surroundin said impeller hub, said sleeve being internallytangent to said hub and externally tangent to said inner wall of thecasing and free to rotate about its own center with the points oftangency substantially fixed at diametrically opposite sides of the axisof the casing, whereby said working space is divided into two chambersthe cross sections of which comprise complementary oppositely facinginterlocking lunes, a radially extending vane carried by said hub andconstituting the effective moving part of the impeller member, said vanepassing through a slot in said sleeve with its outer end having asliding fit with the inner peripheral wall of the casing, whereby therotation of the impeller member and the sleeve causes a progressive andalternate division of the respective lune-shaped chambers intosuccessively waxing and waning fluid receiving and fluid dischargingportions, the discharging portions in the case of both chambers being inadvance of said vane and the receiving portions rearward thereofconsidering the direction of rotation, means for independently supplyingfluid to the fluid receiving portions, said annular sleeve being hollowproviding an annular chamber, said chamber opening toward the forwardface of the vane to receive fluid from said discharge portions, anexhaust chamber disposed at one end of said working chamber, one end ofsaid sleeve projecting through a slot in the casing communicating withsaid exhaust chamber, and a plurality of openings in said end of thesleeve for discharging fluid into said exhaust chamber, said openingsbeing provided by intervening streamlined curved partitions soconstructed and arranged that said openings are directed tangentiallyand are of an expanding cross section and serve to direct the fluid intosaid exhaust chamber to create a centrifugal swirl therein, and meansfor driving said impeller.

26. A rotary pump of the class described, comprising, in combination, acasing containing a substantially cylindrical working chamber, a hollowhub rotatable concentrically of said casing, a hollow cylindrical ringmounted for rotation in said chamber in bearings eccentric to saidchamber and said hub, a longitudinally extending slot in said ring, aradially extending vane carried by said hub, projecting through saidslot in said ring, and adapted to sweep the inner wall of said chamberduring such operation, an opening in the edge of the slot adjacent theforward face of the vane for admitting fluid from the chamber to theinterior of said ring, outlet connections leading from said ring, theopposite edge of said slot being imperforate, a concavity in saidforward face of.

inner circumferential wall of said casing, the

hollow interior of said hub providing a fluid transfer chamber, anannular hollow double-walled rotatable sleeve of substantiallyrectangular longitudinal cross section surrounding said impeller hub andproviding a fluid transfer chamber within the hollow interior of thesleeve, longitudinally spaced end walls also bounding said last namedfluid transfer chamber, an axially extending rectangular slot in oneside of said sleeve, said slot being longitudinally coextensive with thesaid working space of the pump, a radially extendingvane carried by saidhub for rotation therewith, said vane being substantially rectangular incross section, passing through said slot, and of dimensions to have aneasy working flt therein, the edges of the outer portion of said vanehaving a sliding substantially fluid-tight fit with the inner wells ofthe casing bounding said working space, a radial wall provided on saidsleeve at one side of said slot confining the hollow interior at thatpoint, while at the opposite side of the slot a longitudinally elongatedopening faces the adjacent side of the vane providing free communicationwith the hollow interior of said sleeve, the intermediate portion ofsaid last named side of the vane being radially concave for an extentgreater than the thickness of said sleeve, thus permitting flow betweensaid sleeve opening and the working space upon either side of thesleeve, the opposite side wall of said vane facing the adjacentconflning wall of the sleeve being radially concave for an extentgreater than the thickness of said sleeve, and an opening through theradially inward portion of said vane providing communication between thelast mentioned concave portion and the interior of the hollow hub fromwhich the vane extends, thereby permitting flow between the interior ofsaid hollow hub and the working space on either side of the sleeve,means for furnishing fluid to and receiving it from said fluid transferchambers.

28. A rotary pump comprising, in combination, a substantiallycylindrical casing, an impeller member rotatably mounted within saidcasing and coaxially therewith, said impeller member comprising acentral substantially cylindrical hollow hub forming a substantiallyannular working space of uniform radius between the hub and the innercircumferential wall of said casing, the hollow interior of said hubproviding a fluid transfer chamber, an annular hollow double-walledrotatable sleeve of substantially rectangular longitudinal cross sectioneccentrically surrounding said impeller hub and providing a fluidtransfer chamber within the hollow interior of the sleeve,longitudinally spaced end walls also bounding said last named fluidtransfer chamber, means rotatably mounting said sleeve so that it isinternally tangent to said hub and externally tangent to said inner wallof the casing, and free to rotate about its own center with the pointsof tangency substantially flxed at diametrically opposite sides of theaxes of the casing, whereby said working space is divided into twochambers the cross sections of which comprise complementary oppositelyfacing interlocking lunes, an axially extending rectangular slot in oneside of said sleeve, said slot being longitudinally coextensive with thesaid working space of the pump, a radially extending vane carried bysaid hub for rotation therewith, said vane being substantiallyrectangular in cross section, passing through said slot, and ofdimensions to have an easy workingfit therein, the edges of the outerportion of said vane having a sliding substantially fluid-tight flt withthe inner walls of the casing bounding said working space, whereby therotation of the impeller member and the sleeve causes a progressive andalternate division of the respective lune-shaped chambers intosuccessively waxing and waning fluid receiving and fluid dischargingportions, the discharging portions in the case of both chambers being inadvance of said vane and the receiving portions rearward thereofconsidering the direction of rotation, a radial wall provided on saidsleeve at one side of said slot confining the hollow interior at saidpoint, while at the opposite side of the slot a longitudinally elongatedopening faces the adjacent side of the vane providing free communicationwith the hollow interior of said sleeve, the intermediate portion ofsaid last named side of the vane being radially concave for an extentgreater than the thickness of said sleeve, thus permitting flow be- 25tween said sleeve opening and the fluid receiving and dischargingsections of the lune-shaped chambers upon either side of the sleeve, theopposite side wall of said vane facing the adjacent confining wall ofthe sleeve being radially concave for an extent greater than thethickness of said sleeve, and an opening through the radially inwardportion of said vane providing communication between the last namedconcavity and the interior of the hollow hub from which the vaneextends, thereby permitting flow between the interior of said hollow huband the fluid receiving and discharging sections of the lune-shapedchambers on either side of the sleeve, means for furnishing fluid to andreceiving it from said fluid transfer chambers.

' ERIK G. SEASTROM.

REFERENCES CITED The following references are of record in the file ofthis patent:

UNITED STATES PATENTS Number Number Name Date Schroder Mar. 21, 1893Smith Mar. 31, 1903 Mooney May 19, 1908 Nielsen Mar. 3, 1914 GallingsApr. 23, 1918 Westin Apr. 28, 1925 Ungar Jan. 25, 1944 FOREIGN PATENTSCountry Date Switzerland 1930 Great Britain June 29, 1922 Great Britain1929

